JP3694575B2 - Heat utilization system using hydrogen storage alloy - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention repeatedly stores and releases hydrogen in a hydrogen storage alloy to obtain cold using the endothermic effect that occurs during the release of hydrogen, or obtains warmth using the heat dissipation effect that occurs during the storage of hydrogen. The present invention relates to a heat utilization system using a hydrogen storage alloy.
[0002]
[Prior art]
A heat utilization system using a conventional hydrogen storage alloy using a hydrogen storage alloy will be described with reference to FIG. The heat pump cycle J1 using a hydrogen storage alloy used a shell & tube type heat exchanger to obtain heating, heat dissipation and cold output of the hydrogen storage alloy J2.
The heat pump cycle J1 shown in this prior art uses four shell and tube type heat exchangers J3 to J6, and each heat exchanger J3 to J6 can exchange heat between the hydrogen storage alloy J2 and the heat medium. Is provided. The hydrogen storage alloys J2 of the first and second heat exchangers J3 and J4 communicate with each other through a hydrogen passage, and the hydrogen storage alloys J2 of the third and fourth heat exchangers J5 and J6 also communicate with each other through a hydrogen passage. Is provided.
[0003]
The operation supplies a heat medium for heating to the first heat exchanger J3 and a heat medium for heat dissipation to the second heat exchanger J4. Then, hydrogen from the first heat exchanger J3 is released and stored in the second heat exchanger J4. That is, hydrogen driving is performed.
Next, the heating heat medium supplied to the first heat exchanger J3 is switched to the heat dissipating heat medium, and the heat dissipating heat medium supplied to the second heat exchanger J4 is supplied. , And supply by switching to a heat medium for cold output. Then, the first heat exchanger J3 occludes hydrogen and the second heat exchanger J4 releases hydrogen. When the second heat exchanger J4 releases hydrogen, the heat medium for cooling output is cooled. That is, a cold output is obtained.
Then, the above cycle is repeated.
[0004]
On the other hand, when the cooling heat output is obtained from the second heat exchanger J4, a heating heat medium is supplied to the third heat exchanger J5 and a heat dissipation heat medium is supplied to the fourth heat exchanger J6. . Then, hydrogen of the third heat exchanger J5 is released and stored in the fourth heat exchanger J6. That is, when the first and second heat exchangers J3 and J4 are obtaining the cold output, the third and fourth heat exchangers J5 and J6 are driven with hydrogen.
Next, the heating heat medium supplied to the third heat exchanger J5 is switched to the heat dissipating heat medium, and the heat dissipating heat medium supplied to the fourth heat exchanger J6 is supplied. , And supply by switching to a heat medium for cold output. Then, the third heat exchanger J5 occludes hydrogen and the fourth heat exchanger J6 releases hydrogen. When the fourth heat exchanger J6 releases hydrogen, the heat medium for cold output is cooled. That is, when the first and second heat exchangers J3 and J4 are driven with hydrogen, the third and fourth heat exchangers J5 and J6 can obtain cold output.
Then, the above cycle is repeated.
[0005]
[Problems to be solved by the invention]
The heat exchangers J3 to J6, which exchange heat between the hydrogen storage alloy J2 and the heat medium, are large in size because of the shell and tube type used. Since the exchangers J3 to J6 are required, there is a problem that the heat pump cycle J1 becomes large.
[0006]
Further, in the conventional heat pump cycle J1, in order to supply each heat exchanger J3 to J6 with a heat medium for heating and a heat medium for heat radiation, or a heat medium for heat radiation and a heat medium for cooling output, by switching, A large number of switching valves J7 to J14 are required. As described above, when a large number of switching valves J7 to J14 are used, the failure probability increases, which hinders improvement in durability. Further, since the switching valves J7 to J14 are switched at a relatively high frequency, there is a problem that the operation noise is conspicuous.
[0007]
OBJECT OF THE INVENTION
The present invention has been made in view of the above circumstances, and its purpose is to eliminate the need for a switching valve for switching the heat medium that exchanges heat with the hydrogen storage alloy, and to reduce the size and increase the efficiency of the heat pump cycle. It is in the provision of a heat utilization system using a possible hydrogen storage alloy.
[0008]
[Means for Solving the Problems]
  The heat utilization system using the hydrogen storage alloy of the present invention employs the following technical means in order to achieve the above object.
(Means of Claim 1)
  A heat utilization system using a hydrogen storage alloy uses heat absorption when hydrogen is released from the hydrogen storage alloy, or heat dissipation when hydrogen is stored.
  Using a plurality of cells including a flat first chamber filled with a hydrogen storage alloy, a first chamber connected to the first chamber through a hydrogen passage, and a flat second chamber filled with a hydrogen storage alloy,
  This multiple cellsAround the axis of rotationPlaced inThe plurality of cellsBy rotating, the heat medium that touches the first chamber and the heat medium that touches the second chamber are changed, and the first chamber is changed to the second chamber, or the second chamber is changed to the first chamber. Provided to move hydrogen to,
  Each first chamber is disposed in the axial direction of the rotation axis with respect to each second chamber, and the hydrogen passage communicates the first chamber and the second chamber separated in the axial direction of the rotation shaft. ,
  The first chamber and the second chamber are disposed away from the radial direction as they extend outward from the rotation center of the cell.
[0009]
(Means of Claim 2)
In the heat utilization system using the hydrogen storage alloy of claim 1,
The first chamber and the second chamber have a gap of substantially the same width through which a heat medium can pass between the other adjacent first and second chambers, and are arranged at the rotation centers of the plurality of cells. Arranged in a spiral around the axis of rotation,
A heat medium is provided in the gap so as to flow.
[0010]
(Means of claim 3)
In the heat utilization system using the hydrogen storage alloy according to claim 1 or 2, the second chamber is provided by being divided into a plurality through a hydrogen passage,
The heating medium that touches each second chamber is changed by the rotation of the cell, hydrogen is moved from the divided second chamber to another second chamber, and hydrogen is transferred from the divided second chamber to the first chamber. And a plurality of cold outputs are obtained from the plurality of second chambers during one rotation of the cell.
[0011]
Operation and effect of the invention
(Operation and effect of claim 1)
The plurality of cells are driven to rotate by the cell moving means, and the first chamber and the second chamber of each cell are brought into contact with different heat media to move hydrogen.
As a specific example, when the first chamber is brought into contact with a heating medium for heating, the first chamber is heated and the hydrogen storage alloy releases hydrogen. At this time, when the second chamber is brought into contact with a heat dissipation heat medium, the hydrogen storage alloy in the second chamber stores hydrogen. That is, hydrogen moves from the hydrogen storage alloy in the first chamber to the hydrogen storage alloy in the second chamber.
Next, when the first chamber is brought into contact with a heat-dissipating heat medium, the first chamber receives a temperature drop due to heat dissipation, and the hydrogen storage alloy stores hydrogen. At this time, hydrogen is released from the hydrogen storage alloy in the second chamber in a state where the second chamber is in contact with the heat medium for cold output. Then, the heat medium for cold output is cooled, and a cold output is obtained.
[0012]
The heat utilization system using the hydrogen storage alloy of the present invention does not perform heat exchange with the hydrogen storage alloy by switching the type of the heat medium in contact with the hydrogen storage alloy, but by rotating and moving the cell, the hydrogen storage alloy itself Since the type of the heat medium that moves and contacts is changed, a switching valve for switching the type of the heat medium is not required as in the prior art. Thus, since the switching valve is not required, it is possible to reduce the operating noise for switching the heat medium, reduce the failure probability, and improve long-term reliability.
[0013]
  Since a configuration is adopted in which a plurality of cells having flat first and second chambers are rotated and the heat medium that touches the first and second chambers is switched, the physique of the heat pump cycle can be made smaller than before.
  In addition, the first and second chambers provided flatlyPlaced away from the radial direction as it extends outward from the center of cell rotationTherefore, the contact area between the first and second chambers and the heat medium is increased, and there are fewer gaps compared to the type in which the first and second chambers are arranged radially, and the hydrogen storage alloy in the same volume Distribution density increases.
  For this reason, the rotation diameter dimension of a cell can be made small and the physique of a heat pump cycle can be miniaturized very much. Alternatively, the heat exchange efficiency in the heat pump cycle can be improved by increasing the contact area between the first and second chambers and the heat medium and increasing the distribution density of the hydrogen storage alloy.
[0014]
(Operation and effect of claim 2)
Since the first and second chambers are arranged in a state of being wound around the rotation axis, the gap in the rotation range of the cell becomes very small, the distribution density of the hydrogen storage alloy greatly increases, and as a result, the heat pump cycle Heat exchange efficiency can be improved.
In addition, since the heat medium flows through the gap and the gap through which the heat medium passes is provided with substantially the same width, the flow of the heat medium flowing along the first and second chambers is rectified and the flow velocity Will be faster. By increasing the flow rate of the heat medium, the amount of heat exchange between the heat medium and the hydrogen storage alloy increases, and the heat exchange efficiency of the heat pump cycle can be increased.
[0015]
(Operation and effect of claim 3)
Since the second chamber is divided into a plurality and provided so as to obtain a plurality of cooling outputs from the plurality of second chambers during one rotation of the cell, the cooling efficiency of the heat pump cycle can be increased.
[0016]
DETAILED DESCRIPTION OF THE INVENTION
Next, embodiments of the present invention will be described based on examples and modifications.
[Configuration of the first embodiment]
In the first embodiment, the heat utilization system using the hydrogen storage alloy of the present invention is applied to a cooling device for indoor air conditioning. This first embodiment will be described with reference to FIGS.
[0017]
(General description of the cooling device 1)
A schematic configuration of the cooling device 1 of the present embodiment will be described with reference to FIG. In this example, a two-stage cycle was used as an example of the heat pump cycle 2 using a hydrogen storage alloy. In the two-stage cycle, the second chamber of the present invention is divided, hydrogen is transferred from the first chamber to one of the second chambers, and one second chamber is transferred to the other second chamber. The hydrogen is moved to obtain a first-stage cold output, and the hydrogen is moved from the other second chamber to the first chamber to obtain a second-stage cold output, which will be described in detail later.
[0018]
The cooling device 1 to which the present embodiment is applied is broadly divided into a heat pump cycle 2 using a hydrogen storage alloy, and heated water for heating the hydrogen storage alloy (corresponding to a heating medium for heating, water in this embodiment). Produced by the combustion device 3 for generating hydrogen, the facility water cooling means 4 for cooling the facility water for cooling the hydrogen storage alloy (water in this embodiment, which corresponds to the heat medium for heat dissipation), and the hydrogen releasing action of the hydrogen storage alloy. The indoor air conditioner 5 for air-conditioning the room with cold output water cooled by the absorbed heat (corresponding to a heat medium for cold output, in this embodiment), and a control device 6 for controlling each electric functional component mounted It consists of.
[0019]
The heat pump cycle 2, the combustion device 3, the facility water cooling means 4, and the control device 6 are installed outdoors as an outdoor unit 7, and an indoor air conditioner 5 is arranged indoors. The cooling device 1 shown in the present embodiment is a so-called multi-air conditioner in which a plurality of indoor air conditioners 5 can be connected to one outdoor unit 7.
[0020]
(Description of heat pump cycle 2)
The heat pump cycle 2 of this embodiment uses a two-stage cycle as described above. As shown in FIG. 1, the upper chamber S1 (corresponding to the first chamber) in which a hydrogen storage alloy is enclosed, The middle chamber S2 (corresponding to the second chamber) in which the hydrogen storage alloy is sealed is communicated with the upper chamber S1 through the hydrogen passage S4, and the hydrogen storage alloy is communicated with the middle chamber S2 through the hydrogen passage S4. A plurality of cells S provided with a lower chamber S3 (corresponding to the second chamber) in which is enclosed. In this embodiment, 12 to 18 cells S were used.
[0021]
Three types of hydrogen storage alloys with different hydrogen equilibrium pressures were used. In the upper chamber S1, high temperature hydrogen storage alloy (hereinafter referred to as high temperature alloy HM) powder with the same equilibrium hydrogen pressure and the highest hydrogen equilibrium temperature was used. Enclosed, medium temperature hydrogen storage alloy (hereinafter referred to as intermediate temperature alloy MM) powder is enclosed in the middle chamber S2, and the low temperature hydrogen storage alloy (the hydrogen equilibrium temperature is the lowest at the same equilibrium hydrogen pressure) in the lower chamber S3. Hereinafter, the powder of the low temperature alloy LM) is encapsulated.
This will be explained using the PT refrigeration cycle of FIG. 6. The characteristics of the hydrogen storage alloy are relatively high temperature side (left side in the figure), high temperature alloy HM, low temperature side is low temperature alloy LM, both Intermediate temperature alloy MM is in the middle.
[0022]
One cell S is formed of a cell container (upper, middle and lower chambers S1, S2, S3 and hydrogen passage S4) by a joining method such as vacuum brazing or welding using a metal having no hydrogen permeation such as stainless steel or copper. The container is filled in the middle, filled with powdered hydrogen storage alloy, evacuated, activated, filled with hydrogen at high pressure, and the opening covered with a metal lid It is sealed by welding.
As shown in FIGS. 3 and 4, the outer shape of one cell S is a flat container-like upper, middle, and lower side chambers S1, S2, and S3 each having a rod-like shape having a hydrogen passage S4 formed therein. It has a shape connected by the connecting portion S5.
[0023]
Each of the upper, middle, and lower chambers S1, S2, and S3 is provided with an arc shape in addition to the flat shape, so that one surface is provided with a convex curve and the other surface is opposed to each other. It is provided to be curved in a concave shape. In addition, in each of the upper, middle, and lower chambers S1, S2, and S3, a number of pressure-resistant columns (not shown, for example, corrugated fins, offset fins, etc.) are provided in a joined state.
By being provided in this manner, tensile stress and compressive stress are applied to the opposing surfaces of each chamber under a low pressure during evacuation and under a high pressure during hydrogen filling, and the distance between the opposing surfaces can be reduced to a number of pressure-resistant columns. Therefore, the deformation of each chamber is kept small, and as a result, a flat chamber is realized.
[0024]
In each of the plurality of cells S, the connecting portions S5 of the plurality of cells S are fixed around the rotation shaft 8 having a substantially cylindrical shape. The rotating shaft 8 is rotationally driven by a cell moving means (not shown). The cell moving means is a motor that rotates a plurality of cells S slowly and continuously (for example, 20 per hour). About laps).
The flat, upper, middle, and lower chambers S1, S2, and S3 fixed to the rotating shaft 8 are arranged away from the radiation as they extend outward from the rotating shaft 8 (see FIG. 5).
Specifically, each of the upper, middle, and lower chambers S1, S2, and S3 is provided with gaps of substantially the same width between the adjacent upper, middle, and lower chambers S1, S2, and S3. It is arranged in a spiral shape wound around in an arc shape. The gap can pass through the heat medium. In this embodiment, the gap is provided so that the heat medium flows through the gap.
[0025]
In this embodiment, a divider 9 is provided around each chamber in order to make the heat medium flowing through the gap efficiently contact the upper, middle, and lower chambers S1, S2, and S3. This divider 9 reduces the heat dissipation loss of the heat medium by flowing the heat medium along each chamber, and also rectifies the flow of the heat medium to increase the flow rate and increase the heat exchange efficiency. In addition, avoiding the problem that the facing surface of the chamber S touches a different heat medium at the boundary where the cell S circulates the hydrogen driving unit α → first cooling output unit β → second cooling output unit γ, which will be described later. This increases the heat exchange efficiency.
[0026]
The divider 9 covers each chamber and is provided with a resin material having excellent heat insulation. A plurality of heat medium passages 9 a are formed on the inner surface of the divider 9 to allow the heat medium to flow along the chamber. The heat medium passage 9a is provided in a substantially groove shape, and is provided at a certain depth and width along the flow direction in order to rectify the flow of the heat medium and increase the flow velocity. In addition, a supply / discharge port 9b through which heat medium is supplied to and discharged from the heat medium passage 9a is provided at the outer end and the center side upper part of the divider 9. In this embodiment, the supply / discharge port 9b at the outer end is a supply port that guides the heat medium to the heat medium passage 9a, and the center supply / discharge port 9b discharges the heat medium that has passed through the heat medium passage 9a. It is an exit.
[0027]
As shown in FIG. 1, the heat pump cycle 2 of the two-stage cycle includes a hydrogen driving unit α for forcibly moving the hydrogen in the upper chamber S1 into the lower chamber S3 and the hydrogen moved in the lower chamber S3 in the middle stage. A first cold output unit β that moves to the chamber S2 and a second cold output unit γ that moves the hydrogen that has moved into the middle chamber S2 to the upper chamber S1 are provided.
The hydrogen driving unit α, the first cooling output unit β, and the second cooling output unit γ are provided at approximately 120 ° intervals, and are partitioned by the arrangement of recesses M1 and M2 to be described later.
[0028]
The hydrogen drive unit α has a heating area α1 in which heated water (for example, about 80 ° C.) is supplied in contact with the upper chamber S1, and a middle pressure area α2 in which pressurized water (for example, about 56 ° C.) is in contact with the middle chamber S2. , A lower heat radiation area α3 to which the facility water (for example, about 28 ° C.) in contact with the lower chamber S3 is supplied.
The first chiller output unit β is an upper stage boosted region β1 that is supplied with pressurized water (for example, about 58 ° C.) in contact with the upper chamber S1, and a middle stage that is supplied with facility water (for example, about 28 ° C.) that is in contact with the middle chamber S2. A heat radiation area β2 and a lower-stage cold / heat output area β3 in which cold-heat output water (for example, about 13 ° C.) in contact with the lower-stage chamber S3 is output.
The second cold heat output unit γ outputs the upper heat radiation area γ1 supplied with the facility water (for example, about 28 ° C.) in contact with the upper chamber S1, and the cold output water (for example, about 13 ° C.) in contact with the middle chamber S2. It has a middle-stage cooling / heating output region γ2. It should be noted that the temperature of the heat medium in contact with the lower chamber S3 in the second cooling output unit γ is not questioned, and that part is defined as a questionable region γ3.
[0029]
Then, when the rotating shaft 8 is rotated by a cell moving means (not shown), the group of the upper chamber S1 circulates in the heating region α1 → the upper pressure boosting region β1 → the upper heat radiation region γ1, and the group of the middle chamber S2 becomes the middle stage. The boosting region α2 → the middle heat radiation region β2 → the middle cooling / heating output region γ2 circulates, and the group of the lower chamber S3 circulates the lower heat radiation region α3 → the lower cooling energy output region β3 → the unquestioned region γ3.
[0030]
The group of the upper chamber S1 is covered with the upper container K1, and is provided with a heating area α1, an upper pressure increasing area β1, and an upper heat radiation area γ1. The group of the middle chamber S2 is covered with the middle vessel K2, and is provided with a middle pressure region α2, a middle heat radiation region β2, and a middle cooling output region γ2. Further, the group of the lower chamber S3 is covered with the lower container K3, and a lower heat radiation region α3, a lower cooling output region β3, and an unquestioned region γ3 are provided therein.
[0031]
The upper container K1, the middle container K2, and the lower container K3 are containers K (for example, resin containers) that are continuously connected to each other. As shown in FIG. Sixteen heat medium pipes 10 for supplying and discharging the heat medium are connected to the lower containers K1, K2, and K3. Specifically, six heating medium pipes 10 are connected to the upper container K1 for the heating region α1, the upper pressure increasing region β1, and the upper heat radiating region γ1. β2 is connected to six heat medium pipes 10 for the intermediate cooling power output area γ2, and the lower container K3 is connected to four heat medium pipes 10 for the lower heat radiation area α3 and the lower cooling power output area β3. Yes.
[0032]
In the upper, middle and lower containers K1, K2 and K3, the heat medium supplied by the heat medium pipe 10 is respectively connected to the hydrogen driving part α, the first cold output part β and the second cold output part γ. A recess M1 leading to the supply / discharge port 9b (outer end) of the divider 9 in the area and a recess M2 for collecting the heat medium discharged from the supply / discharge port 9b (center side) are provided. The heat medium to be supplied and discharged is provided so as to be directly supplied and discharged into the divider 9 within a predetermined range (hydrogen drive unit α, first cold output unit β, and second cold output unit γ at approximately 120 ° intervals). ing.
The supply / discharge port 9b provided in each divider 9 rotates in contact with or close to the inner wall of the container K not provided with the recesses M1 and M2, and the inner wall is rotated by the hydrogen drive unit α and the first cold output. This is a partition for the part β and the second cooling output part γ.
Further, in this embodiment, as shown in FIG. 1, an example is shown in which the heat medium flows from the outer supply / discharge port 9b → the heat medium passage 9a → the central supply / discharge port 9b. May be.
[0033]
(Description of other components in the heat pump cycle 2)
Reference numeral 11 shown in FIG. 2 is a booster water circulation path for circulating the booster water to the upper booster region β1 and the middle booster region α2, and the booster water is circulated by the booster water circulation pump P1 'provided in the middle. Note that the pressurized water is water that has risen in temperature due to heat transfer from the upper chamber S1 and the upper vessel K1 in the heating zone α1. During operation of the heat pump cycle 2, the pressurized water in the upper pressure zone β1 is used. The temperature is, for example, about 58 ° C., and the temperature of the pressurized water in the middle stage boosted region α 2 is, for example, about 56 ° C.
[0034]
(Description of combustion device 3)
The combustion apparatus 3 of the present embodiment uses a gas combustion apparatus that burns gas as a fuel to generate heat, and heats heated water with the generated heat. The gas burner 12 performs gas combustion, and the gas burner. A gas supply circuit 15 having a gas amount adjusting valve 13 and a gas opening / closing valve 14 for supplying gas to the gas 12, a combustion fan 16 for supplying combustion air to the gas burner 12, and heat exchange between the combustion heat of the gas and the heating water It comprises a heat exchanger 17 and the like.
The heated water is heated to, for example, about 80 ° C. with the heat obtained by gas combustion of the gas burner 12, and the heated heated water is supplied to the heating zone α1 through the heated water circulation path 18 equipped with the heated water circulation pump P1. To do.
The heating water circulation pump P1 of this embodiment is a tandem pump that is driven by a dual-purpose motor that drives the pressurized water circulation pump P1 '. For this reason, when heated water is supplied from the combustion device 3 to the heat pump cycle 2, the pressurized water is also provided so as to circulate.
[0035]
(Description of indoor air conditioner 5)
The indoor air conditioner 5 is arranged indoors as described above, and forcibly exchanges heat between the indoor heat exchanger 19 and cold output water supplied to the indoor heat exchanger 19 and room air. An indoor fan 20 is provided for blowing the air after heat exchange into the room. The indoor heat exchanger 19 is connected to a cooling output water circulation path 21 for circulating cooling output water supplied from the lower cooling output area β3 and the middle cooling output area γ2, and is in the middle of the cooling output water circulation path 21 (the outdoor unit 7 Inside), a cold output water pump P2 for circulating the cold output water is provided.
[0036]
(Description of facility water cooling means 4)
The facility water cooling means 4 is a water-cooled open type cooling tower, and the facility water cooled by the facility water cooling means 4 is converted into a lower radiating area α3 and a middle radiating area by a facility water circulation path 22 provided with a facility water circulation pump P3. β2 is supplied to the upper heat radiation area γ1.
The facility water cooling means 4 flows the facility water that has passed through the lower radiating region α3, the middle radiating region β2, and the upper radiating region γ1 from the upper side to the lower side, and exchanges heat with the outside air while flowing to radiate heat. In the meantime, it is partially evaporated to remove the heat of vaporization from the facility water flowing at the time of evaporation and cool the flowing facility water. The facility water cooling means 4 includes a heat dissipation fan (not shown), and is provided so as to promote evaporation and cooling of the facility water by the air flow generated by the heat dissipation fan.
In this embodiment, a water-cooled open type cooling tower is shown as the facility water cooling means 4, but a water-cooled sealed type or an air-cooled sealed type in which the facility water (heat-dissipating heat medium) exchanges heat without touching the air. A cooling means may be used.
[0037]
Here, the heating water circulation path 18, the cooling / heating output water circulation path 21 and the facility water circulation path 22 described above are provided with cis-turns T 1, T 2, T 3, respectively, and the water levels in the cis-turns T 1, T 2, T 3 are lowered below a predetermined water level. Then, the water supply valves T4, T5, and T6 provided to the respective valves are opened to replenish the tap water supplied from the water supply pipe 23 into the cisterns T1, T2, and T3.
Further, a drain pan P is disposed at the lower part of the heat pump cycle 2 and is provided so as to drain the drain water generated in the heat pump cycle 2 from the drain pipe 24. The water overflowing from the facility water cooling means 4 is also provided to drain from the drain pipe 24.
[0038]
(Description of the control device 6)
The control device 6 responds to an operation instruction from a controller (not shown) provided in the indoor air conditioner 5 and an input signal of each of a plurality of sensors provided, and the above-described heated water circulation pump P1 (pressurized water circulation pump P1 ′). , Cooling output water pump P2, facility water circulation pump P3, water supply valves T4, T5, T6, electrical function components such as the heat dissipation fan of the facility water cooling means 4, and electrical function components of the combustion device 3 (combustion fan 16, gas amount adjustment) Valve 13, gas on-off valve 14, ignition device (not shown), and the like, and an operation instruction for the indoor fan 20 is given to the indoor air conditioner 5.
[0039]
(Description of cooling operation)
The operation of the cooling operation by the cooling device 1 will be described with reference to the PT refrigeration cycle diagram of FIG.
When the cooling operation is instructed by the controller of the indoor air conditioner 5, the control device 6 causes the combustion device 3, the cell moving means, the heat radiating fan, the heating water circulation pump P1 (pressure-boosting water circulation pump P1 '), the cold heat output water pump P2, and the heat radiation. The water circulation pump P3 is activated and the indoor fan 20 of the indoor air conditioner 5 instructed to be cooled is turned on.
[0040]
The plurality of cells S rotate and move slowly and continuously by the cell moving means. As a result, the plurality of cells S move in the order of the hydrogen driving unit α → the first cooling output unit β → the second cooling output unit γ.
That is, each upper chamber S1 moves in the order of heating zone α1 → upper pressure boosting region β1 → upper heat dissipation zone γ1, and each middle chamber S2 moves in the order of middle boosting zone α2 → middle heat dissipation zone β2 → middle cooling heat output zone γ2. Each lower chamber S3 moves in the order of the lower heat radiation area α3 → the lower cooling output area β3 → the unquestioned area γ3.
[0041]
In the cell S that has entered the hydrogen drive unit α, the upper chamber S1 touches the heated water, the middle chamber S2 touches the pressurized water, and the lower chamber S3 touches the facility water.
When the upper chamber S1 comes into contact with heated water (80 ° C.), the internal pressure of the upper chamber S1 rises and the high temperature alloy HM releases hydrogen.
When the middle chamber S2 touches the pressurized water (56 ° C.), the internal pressure of the middle chamber S2 rises to a pressure at which the intermediate temperature alloy MM does not occlude hydrogen.
When the lower chamber S3 comes into contact with the facility water (28 ° C.), the internal pressure of the lower chamber S3 decreases, and the low temperature alloy LM occludes hydrogen.
[0042]
Thus, the upper chamber S1 touches the heated water in the heating zone α1, the middle chamber S2 touches the pressurized water in the middle boosted region α2, and the lower chamber S3 touches the hot water in the lower heat radiating zone α3, thereby causing the upper chamber S1 to touch. The inside is 80 ° C; 1.0 MPa, the inside of the middle chamber S2 is 56 ° C; 1.0 MPa, the inside of the lower chamber S3 is 28 ° C; 0.9 MPa, and the high temperature alloy HM in the upper chamber S1 releases hydrogen (see FIG. 6). (1)), the low temperature alloy LM in the lower chamber S3 occludes hydrogen ((2) in FIG. 6). The middle chamber S2 is heated by the pressurized water and has a high internal pressure, and the intermediate temperature alloy MM does not occlude hydrogen.
And the cell S which passed the hydrogen drive part (alpha) moves to the 1st cold-heat output part (beta) after that.
[0043]
In the cell S that has entered the first cold output unit β, the upper chamber S1 touches the pressurized water, the middle chamber S2 touches the facility water, and the lower chamber S3 touches the cold output water.
When the upper chamber S1 comes into contact with the pressurized water (58 ° C.), the internal pressure of the upper chamber S1 rises to a pressure at which the high temperature alloy HM does not occlude hydrogen.
When the middle chamber S2 comes into contact with the facility water (28 ° C.), the internal pressure of the middle chamber S2 decreases, the intermediate temperature alloy MM occludes hydrogen, and the low temperature alloy LM in the lower chamber S3 releases hydrogen.
Since the low temperature alloy LM releases hydrogen, an endothermic heat is generated in the lower chamber S3, and the cold output water touching the lower chamber S3 is cooled to, for example, 13 ° C. The low temperature alloy LM is provided such that the internal pressure of the lower chamber S3 is higher than the internal pressure of the intermediate chamber S2 when the cold output water is about 13 ° C.
[0044]
Thus, the upper chamber S1 touches the pressurized water in the upper pressure boosting region β1, the middle chamber S2 touches the facility water in the middle heat radiating region β2, and the lower chamber S3 touches the cold heat output water in the lower cooling power output region β3. The upper chamber S1 is 58 ° C; 0.5 MPa, the middle chamber S2 is 28 ° C; 0.4 MPa, the lower chamber S3 is 13 ° C; 0.5 MPa, and the low temperature alloy LM in the lower chamber S3 releases hydrogen ( (3) in FIG. 6), the intermediate temperature alloy MM in the middle chamber S2 occludes hydrogen ((4) in FIG. 6). When the low temperature alloy LM in the lower chamber S3 releases hydrogen, it takes heat from the cold output water that touches the lower chamber S3 due to the endothermic effect, and lowers the temperature of the cold output water. The upper chamber S1 is heated by the pressurized water and has a high internal pressure, and the high temperature alloy HM does not occlude hydrogen.
And the cell S which passed the 1st cold output part (beta) moves to the 2nd cold output part (gamma) after that.
[0045]
In the cell S that has entered the second cold output unit γ, the upper chamber S1 touches the facility water, the middle chamber S2 touches the cold output water, and the lower chamber S3 touches the unquestioned water.
When the upper chamber S1 touches the facility water (28 ° C.), the internal pressure of the upper chamber S1 decreases, the high temperature alloy HM occludes hydrogen, and the intermediate temperature alloy MM in the middle chamber S2 releases hydrogen.
Since the intermediate temperature alloy MM releases hydrogen, heat is generated in the middle chamber S2, and the cold output water that touches the middle chamber S2 is cooled to, for example, 13 ° C. The intermediate temperature alloy MM is provided so that the internal pressure of the middle chamber S2 is higher than the internal pressure of the upper chamber S1 when the cold output water is about 13 ° C.
[0046]
Thus, when the upper chamber S1 touches the facility water in the upper radiating zone γ1, the inside of the upper chamber S1 is 28 ° C .; 0.1 MPa, the inside of the middle chamber S2 is 13 ° C .; 0.2 MPa, and the inside of the lower chamber S3 is unquestioned. The intermediate temperature chamber MM in the middle chamber S2 releases hydrogen ((5) in FIG. 6), and the high temperature alloy HM in the upper chamber S1 occludes hydrogen ((6) in FIG. 6). When the intermediate temperature alloy MM in the middle chamber S2 releases hydrogen, the heat is absorbed from the cold output water that touches the intermediate chamber S2 due to the endothermic action, and the temperature of the cold output water is lowered. The temperature of the lower chamber S3 is irrelevant, and the low temperature alloy LM in the lower chamber S3 does not occlude hydrogen.
And the cell S which passed the 2nd cold-power output part (gamma) moves to the hydrogen drive part (alpha) after that.
[0047]
The low-temperature cold output water that has been deprived of heat in the lower and middle cooling output areas β3 and γ2 of the heat pump cycle 2 is supplied to the indoor heat exchanger 19 of the indoor air conditioner 5 via the cooling output water circulation path 21. Then, heat is exchanged with the air blown into the room to cool the room.
[0048]
[Effects of Examples]
The heat pump cycle 2 of the cooling apparatus 1 to which the present invention is applied does not use a plurality of conventional shell and tube type heat exchangers, but collects a plurality of cells S including a plurality of flat chambers, Since it is rotated within K, the physique of the heat pump cycle 2 of this embodiment can be greatly reduced compared to the conventional heat pump cycle using a plurality of shell & tube type heat exchangers. Thus, the outdoor unit 7 of the cooling device 1 can be downsized.
[0049]
In the cooling device 1 of the present embodiment, the cell moving means moves a plurality of cells S instead of switching the type of the heat medium contacting the hydrogen storage alloy and exchanging heat with the hydrogen storage alloy as in the prior art. As a result, the hydrogen storage alloy itself moves to change the type of heat medium (heated water, facility water, pressurized water, cold output water), so there is no need for a switching valve for switching the type of heat medium in the heat pump cycle 2 Become.
Thus, since the cooling device 1 of the present embodiment does not require a switching valve for frequently switching the heat medium in the heat pump cycle 2, the operation noise is reduced as compared with the conventional case, and the failure probability is reduced. Long-term reliability is improved.
[0050]
In particular, in the present invention, the upper, middle, and lower chambers S1, S2, and S3 are arranged away from the radial direction as they extend outward from the center of rotation, and as a specific aspect, spirally around the rotating shaft 8. Since the gaps between the cells S are provided with substantially the same width, there is no useless space in the container K. For this reason, the contact area between each chamber and the heat medium is large, and the distribution density of the high, medium, and low temperature alloys HM, MM, and LM in the container K is greatly increased.
As a result, the rotational diameter dimension of the cell S (the outer diameter dimension of the container K) can be reduced, and the physique of the heat pump cycle 2 can be greatly reduced in size. Alternatively, the efficiency of the heat pump cycle 2 is greatly improved, and the cooling capacity of the cooling device 1 can be increased.
[0051]
In addition, since the flow of the heat medium flowing along the upper, middle, and lower chambers S1, S2, and S3 is rectified and accelerated by the divider 9, the heat exchange loss of the heat medium is reduced, and the cooling efficiency of the heat pump cycle 2 is improved. Can be increased.
Furthermore, the problem that the facing surface of the chamber touches a different heat medium at the boundary where the cell S circulates from the hydrogen driving unit α → the first cooling output unit β → the second cooling output unit γ is avoided, and the heat exchange efficiency is reduced. Can be prevented.
[0052]
[Second Embodiment]
Next, a second embodiment in which the heat utilization system using the hydrogen storage alloy of the present invention is applied to an air conditioner will be described. In addition, FIG. 7 is a schematic block diagram of the air-conditioning apparatus to which this invention is applied.
The air conditioner 30 of the present embodiment guides the heated water heated by the combustion device 3 to the indoor heat exchanger 19 of the indoor air conditioner 5 during the heating operation in addition to the cooling operation shown in the above embodiment. This is for room heating. The heating water circulation path 18 and the cold output water circulation path 21 shown in the first embodiment are connected, and three switching valves V1, V2, V3 (cooling and Heating switching valve).
In addition to the indoor air conditioner 5, it may be connected to a floor heating mat, a bathroom dryer or the like so as to perform floor heating, bathroom heating, etc. by supplying heated water.
[0053]
[Modification]
In the above-described embodiment, an example in which the divider 9 is provided around each chamber is shown, but the divider 9 may not be used.
As a specific example, as shown in FIG. 8, the upper, middle, and lower chambers S1, S2, and S3 are arranged around the rotating shaft 8, and the upper, middle, and lower chambers S1 are arranged. , S2 and S3 and other adjacent upper, middle and lower chambers S1, S2 and S3 may be provided with gaps of substantially the same width so that the heat medium flows through the gaps. Even if the divider 9 is eliminated in this manner, the distribution density of the hydrogen storage alloy in the container K is increased, and the gap is substantially the same width. Therefore, the flow of the heat medium flowing through the gap is rectified and the flow velocity is increased. The heat exchange rate between the heat medium and the hydrogen storage alloy increases, and the heat exchange efficiency of the heat pump cycle 2 can be increased.
[0054]
In the above embodiment, for ease of explanation, the upper chamber S1, the middle chamber S2, and the lower chamber S3 are shown according to the top and bottom of the drawing. You may arrange in other directions, such as inverting. Further, the arrangement of the upper chamber S1, the middle chamber S2, and the lower chamber S3 may be interchanged. Furthermore, the moving direction of the cell S may be reversed. In such a case, as a matter of course, the arrangement positions of the heat media in contact with the chambers are changed so that the heat pump cycle is established.
[0055]
In the above embodiment, as an example of the heating medium for pressure increase, the heating medium (temperature increasing water in the embodiment) in which the temperature is increased by cooling the upper chamber S1 whose temperature has increased in the heating region α1 is shown. You may use the thermal medium heated up by the means (For example, the temperature rise by a combustion apparatus, the temperature rise by an electric heater, the temperature rise using exhaust heat, etc.).
In the above embodiment, an example using a two-stage cycle was shown as an example of the heat pump cycle 2, but it may be used for a one-stage cycle, or three or more second chambers may be divided into three stages. You may use as the above cycle.
[0056]
In the above embodiment, a multi air conditioner in which a plurality of indoor air conditioners 5 can be connected to one outdoor unit 7 is shown. However, the present invention is applied to an air conditioner in which one indoor air conditioner 5 is connected to one outdoor unit 7. It may be applied.
In the above-described embodiment, an example in which the room is cooled with the heat medium for cooling output (cold water in the embodiment) obtained by the heat pump cycle 2 is shown, but the refrigeration operation and the freezing operation are performed with the heating medium for cooling output. The present invention may be used as another cooling device.
[0057]
In the above embodiment, an example using one heat pump unit (a unit in which a plurality of cells S are accommodated in one container K) is shown. However, a plurality of heat pump units are mounted to increase cooling capacity, You may use for the cooling device with which big cooling capacity is requested | required, such as an air conditioning system.
[0058]
In the above embodiment, the gas combustion apparatus for burning gas is used as the heating means for heating the heating medium (heating water in the embodiment), but other combustion such as an oil combustion apparatus for burning oil is used. An apparatus may be used, and other heating means such as a heating means for heating a heat medium for heating by exhaust heat of the internal combustion engine, a steam by a boiler, a heating means using an electric heater, or the like may be used. In addition, when utilizing the exhaust heat of an internal combustion engine, it can also use for vehicles.
[0059]
In the above embodiment, tap water is used as an example of each heat medium, but other liquid heat medium such as antifreeze liquid or oil may be used, or a gas heat medium such as air may be used.
In the above embodiment, the example in which the plurality of cells S are continuously rotated by the cell moving unit has been described, but the cells S may be intermittently rotated.
In the above embodiment, the cooling device that obtains the cold output by the endothermic action when the hydrogen storage alloy releases hydrogen is shown as an example, but the heating that obtains the thermal output by the heat release action when the hydrogen storage alloy absorbs hydrogen. The present invention may be applied to a device (for example, a heating device).
[Brief description of the drawings]
FIG. 1 is an operation explanatory diagram of a heat pump cycle (first embodiment).
FIG. 2 is a schematic configuration diagram of a cooling device (first embodiment).
FIG. 3 is a perspective view of a cell provided with a divider (first embodiment).
FIG. 4 is a partial perspective view of a cell (first embodiment).
FIG. 5 is a perspective view of a cell covered with a divider (first embodiment).
FIG. 6 is a PT refrigeration cycle diagram (first embodiment).
FIG. 7 is a schematic configuration diagram of an air-conditioning apparatus (second embodiment).
FIG. 8 is a diagram of a cell viewed from the axial direction (modified example).
FIG. 9 is a schematic configuration diagram of a cooling device (conventional example).
[Explanation of symbols]
HM high temperature alloy (hydrogen storage alloy)
MM Medium temperature alloy (hydrogen storage alloy)
LM Low temperature alloy (hydrogen storage alloy)
S cell
S1 Upper room (first room)
S2 Middle room (second room)
S3 Lower room (second room)
S4 Hydrogen passage
8 Rotating shaft

Claims (3)

A heat utilization system using a hydrogen storage alloy utilizing heat absorption during hydrogen release of the hydrogen storage alloy or heat dissipation during hydrogen storage,
Using a plurality of cells including a flat first chamber filled with a hydrogen storage alloy, a first chamber communicated with the first chamber through a hydrogen passage, and a flat second chamber filled with a hydrogen storage alloy,
By disposing the plurality of cells around the rotation axis and rotating the plurality of cells, the heat medium that touches the first chamber and the heat medium that touches the second chamber are changed, and the first medium is changed. Provided to move hydrogen from one chamber to the second chamber or from the second chamber to the first chamber ;
Each first chamber is disposed in the axial direction of the rotation axis with respect to each second chamber, and the hydrogen passage communicates the first chamber and the second chamber separated in the axial direction of the rotation shaft. ,
The heat utilization system using a hydrogen storage alloy, wherein the first chamber and the second chamber are disposed away from the radial direction as extending outward from the rotation center of the cell. In the heat utilization system using the hydrogen storage alloy of claim 1,
The first chamber and the second chamber have a gap of approximately the same width through which a heat medium can pass between the other adjacent first and second chambers, and are arranged at the rotation centers of the plurality of cells. Arranged in a spiral around the axis of rotation,
A heat utilization system using a hydrogen storage alloy, characterized in that a heat medium is caused to flow through the gap. In the heat utilization system using the hydrogen storage alloy according to claim 1 or 2,
The second chamber is divided into a plurality through a hydrogen passage,
The rotation of the cell changes the heat medium in contact with each second chamber to move hydrogen from the divided second chamber to the other second chamber and to transfer hydrogen from the divided second chamber to the first chamber. A heat utilization system using a hydrogen storage alloy, wherein a plurality of cold outputs are obtained from a plurality of second chambers during one rotation of the cell.

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